Yarn winding machine



June 26, 1956 F. F. STANGE 2,

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June 26, 1956 F. F. STANGE 2,752,109

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FERDINAND F." STANGE A TTORNEKS med States meme YARN WINDING MACHINE Ferdinand F. Stauge, Westfield, Mass, assiguor to Foster Machine Company, Westfield, Mass, a corporation of Massachusetts Application February 2, 1954, Serial No. 407,691

7 Claims. (Cl. 242-18) This invention relates to a winding machine and particularly to a machine for winding filamentary material, such as yarn, wire or the like. In particular, a machine embodying the present invention is useful for winding yarn of either natural, or synthetic material or a combination of the two.

It is desirable to wind yarn, in many instances, on bobbins to form packages having substantial size. In order to maintain the overall size of such packages within reasonable limits, it is advantageous to begin winding the package on a bobbin having a diameter which is relatively small compared to the diameter of the finished package. These objectives are difiicult to attain in conventional winding machines and involve winding problems relating to the pitch of the yarn as it is being wound on the package and also to the formation of ribbons.

Present day winding machines generally have a traverse roll provided with a suitable cam groove which functions in a dual capacity. The traverse roll not only imparts lateral movement to the yarn, and thus imparts pitch to the winding, but at the same time usually functions as a driver for imparting winding movement to the package. This is customarily obtained by having the package in frictional contact with the tr-averseroll whereby a friction drive is obtained.

This type of drive has several disadvantages. Where the starting diameter of a package is small in comparison to the final diameter of the finished package, the driving ratio between the traverse roll and package will vary-over wide limits. This imposes severe requirements upon the motor or other means for driving the traverse roll. As a rule, the driving problems are such that either larger bobbins are used or the final diameter of the package is smaller than would normally be desired.

This invention makes it possible to provide a winding machine wherein a large ratio of maximum to minimum package diameters is possible without the disadvantages attendant to this arising out of variations in driving ratio. This invention also makes it possible to provide a winder wherein the distance between traverse roll and the surface of the package during winding thereof will remain substantially constant or vary within negligible limits and thus make :it possible to maintain the length 'of unsupported yarn between package and traverse roll generally constant over wide ranges of package diameter. Other advantages arising out of the use of the invention will become apparent to those skilled in the art.

This invention provides a winding machine wherein the traverse roll and package are driven independently of each other, thus endowing the machine with considerable flexibility for control of the winding pitch. This makes it possible to use a small bobbin and wind larger packages. Better control over ribbon formation is also provided. The new invention provides a generally constant clearance between the surface of the package .and the surface of the traverse roll during package winding. This feature is of substantial importance for the reason that closer control over the lay of the yarn is provided.

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In general, this invention provides a traverse roll which may be of conventional design in combination with a separate drive roll for driving the package by frictional contact therewith. The drive roll and traverse roll are mounted so that their axes are parallel and spaced so that the opposed surfaces of the two rolls are separated by a distance less than the diameter of either roll. The axis of the package is mounted parallel to and spaced from the other two axes, the package axis being movable upon part of the surface of a cylinder whose axis is spaced from and parallel to the axes of the drive and traverse rolls and at such a great distance from the surface of the cylinder that said surface does not substantially deviate from a straight line. Inasmuch as a discussion of the more general aspect of the invention is facilitated by reference to drawings, the invention, both in its more general and specific aspects will now be disclosed and described in connection with such drawings. It will be understood that the drawings merely show exemplary embodiment of the invention and the construction illustrated and disclosed may be varied without departing from the invention except as defined by the appended claims.

Figure l is a side elevation, partly in section, of a winding machine embodying the present invention;

Figure 2 is a view, partly in section, along broken line 22 of Figure 1, this view showing details of the pack age brake;

Figure 3 is a sectional detail of the package bobbin;

Figure 4 is a detail on line 44 of Figure 2 illustrating the mounting of the traverse roll shaft;

Figure 5 is a diagrammatic showing of a winding machine embodying the present invention and illustrating the geometrical principles involved, the diagram showing the variation in diameter and position of the package roll during winding;

Figure 6 is a section on line 66 of Figure l illustrating the construction of the traverse roll;

Figure 7 is a section on line 7-7 of Figure 6;

Figure 8 is a side elevation of the traverse roll illustrating the starting slots;

Figure 9 is a perspective view of a portion of one of the molded parts making up the traverse roll.

Figure 10 is a sectional view, similar to that of Figure 6, through a modified traverse roll;

Figure .1-1 is a sectional view taken on the line 11-11 in Figure .10;

Figure 12 is a side elevation of the traverse roll illustrated in Figure 10; and

Figure 13 is a perspective view of a portion of one of the molded parts making up the traverse roll of Figure 10.

The general principles underlying the operation of a machine embodying the present invention may best be understood by referring first to Figure 6. In this figure, drive roll 10 has axis 11 and radius a. The magnitude of radius a is preferably intermediate the radius of a package at the beginning and end of a winding operation. In the event that large packages are to be wound, drive roll 10 may have a radius which is about half of the radius of the finished package. This proportion, however, is not critical and the actual relationship of drive roll radius to finished package roll radius may vary over wide limits and in fact, the drive roll radius may even be larger than the finished package roll radius. However, it is desirable to have the drive roll radius small in order to reduce the size of the parts.

Traverse roll 13 has axis 14 disposed above drive roll axis 11, the axes of the drive roll and traverse roll being parallel. Radius b of the traverse roll may have a value between radius a of the drive roll and the radius of the 3 finished package. It is preferred to have radius b of the traverse roll closer in value to the radius of the finished package and the two radii may be substantially equal. However, it is understood that radius b of the traverse roll may vary within wide limits and may be substantially smaller than the radius of the finished package. It is preferred, however, to have drive roll radius a substantially smaller than traverse roll radius b and have traverse roll radius b somewhat smaller than the finished package radius.

The package axis 15 travels along a path which is designed to maintain the surface of the package at a substantially constant distance from the traverse roll, it having been found that good winding results are obtained when the surface relationship of the package roll and the traverse roll is substantially constant. In order to maintain an absolutely constant distance between the traverse roll and the package roll during the period of winding the package axis should travel along a straight line. However, for the sake of convenience and simplicity of construction, the applicants package axis 15 travels upon a curved path 16 of a cylinder whose axis is 17. The package radius is indicated by c and the cylinder radius from center 17 by d. This radius d is large enough to render the curved path 16 of the package axis 15 of such a small curvature as to be only slightly curved from a straight line. For best results the radius d should be great enough to keep the surface of the package within 1% inches from the surface of the traverse roll and preferably within a range between and of an inch.

For convenience, traverse roll 13 is shown as being disposed above drive roll and offset somewhat to the right. With this arrangement, axis 17 will be disposed below axis 11 of drive roll 10 and somewhat to the left. Axis 17 is parallel to the axes of the drive and traverse rolls. The relative position of these three axes will vary depending upon the relative radii of the drive roll, traverse roll and finished package. However, the arrangement whereby axis 11 of the drive roll is almost in line with axes 17 and 14 has been found to be quite effective. Thus line e between axis 17 and axis 11 will preferably make an angle of almost 180 degrees with line 1 between axes 11 and 14. Package axis is preferably disposed upon that side of the drive roll axis where lines 0 and 1 form an angle somewhat less than 180 degrees. This smaller angle may range from about 165 degrees to about 180 degrees.

Drive roll 10 and'traverse roll 13 are driven by suitable means not shown. It is not necessary that the speed of rotation of traverse roll 13 have any fixed relation to the speed of rotation of drive roll 10. The package will rest upon drive roll 10 and be driven thereby.

By permitting yarn to slip with respect to the traverse roll, pitch control for yarn winding is always possible independently of package size.

Traverse roll 13 and drive roll 10 are mounted so that there is clearance g between the opposed roll surfaces. This clearance g is preferably smaller than radius a of driving roll 15) and about equal to the minimum package radius.

The length of radius d is such that curved portion 16, if extended to the right, would intersect line of centers for the two rolls at a region between the outer surfaces of the two rolls and preferably closer to the surface of roll 10 than to the surface of roll 13. Radius arm a may vary within limits but is preferably of the order of about two times the maximum package radius.

Thus as an example, a machine was constructed Wherein drive roll radius a was 7.5 cm., traverse roll radius b was about 13 cm., while clearance g was about 5 cm. Radius arm d was about 38 cm., while line e was about 29 cm. The angle between line e and line 1 joining the axes of rollers 10 and 13 was about 165 degrees. For the two extreme positions of radius arm at for minimum and maximum package radii, the clearance between the opposed surfaces of the package and traverse roll remained generally constant and within satisfactory limits. The minimum and maximum package radii were about 5 cm. and 10 cm. respectively. Angle x between the two extreme positions of the radius arm for the example given, will be about twice thev angle between the exten sion of line e and center line 1 joining the two roller axes. However, this relationship of clearance between; the package and traverse roll will be found true over a larger angle than shown, this being occasioned by a decrease in the radius of a traverse roll or a wider spread in the radii of the package, or both.

It is possible to have the package arranged so that radius arm d is on the right side of line e. However, the arrangement illustrated is preferred, since it will be evident that a component of the weight of the package roll will be useful for pressing the package against drive roll 11. Furthermore, in the arrangement shown, when radius arm d extends beyond the perpendicular away from line e, the weight component of the package roll will be directed away from the drive roll and may be used to automatically disengage the package roll from the drive roll.

A practical construction embodying the invention diagrammatically illustrated in Figure 5 will now be described in connection with the remaining figures. Thus referring to Figure 1, base generally indicated by numeral 30 is provided. This base may be constructed of suitable castings and provided with suitable journals for supporting the various shafts. In Figure 3, only shaft journals for one shaft end are shown, it being understood that the base has-a part for supporting the other ends of the various shafts.

Journaled in base 30 is dead shaft 31 upon which is rotatively mounted arm 32. Arm 32 is the radius arm and corresponds to radius d of Figure 6. Arm 32 carries at the upper free end 33 thereof a block generally indicated by numeral 34.

Block 34 (see Figure 3) includes block portion 35 carrying package supporting arm 36. Arm 36 may be securely locked in block portion 35 by set screw 37. Arm 36 may have any desired length and is provided with shoulder 38 and end 39 carrying collar 40. Arm 36 has bobbin supporting portion 41 carrying cylindrical form 42. Form 42 has shoulder 43 and has bobbin-supporting outer surface 44. Form 42 is of any suitable material, such as iron or steel or maybe of molded material and has surface 44 finished. Over surface 44, bobbin 45 may be disposed, this bobbin being of paper or any other suitable material. Upon bobbin 45, the yarn for forming package 46 is wound.

As is well understood, bobbin 45 is adapted to be slid in or off form 42 and the bobbin and package are adapted to turn around portion 41. Suitable bearings may be provided for the inside of form 42 for insuring free rotation around portion 41. Form 42 is adapted to be readily removedand replaced by other forms having different diameters or lengths as required.

Referring back to block 34 upon the free end of arm 32 (Fig. 3) additional block parts 47 and 48 are clamped to block portion 35 by suitable means, such as for example, bolts 50. Portions 47 and 48 have rounded internal surfaces for gripping the end of arm 32. Block portions 47 and 48 are also shaped to provide channel 51, extending generally parallel to the axis of arm 32. Lying within channel 51 is rod 53' having top portion 54 (see Fig. 2) extending between slotted bell-crank 55. Slotted bell-crank 55 is pivotally secured at 56 to the general block structure 34, pivot 56 extending generally perpendicular to the axis of rod 53. Flattened portion'54 of rod 53 is secured between the slotted end of crank 55 so that rod 53 may be inoved generally longitudinally when bell-crank 55 is rocked on pivot 56.

Rigidly anchored in bell-crank 55 is handle 57 carry- .7 tension. The entire. machine will operate satisfactorily in any position and the description of the relative vertical positioning of the various axes and shafts is merely a matter of convenience. The relationships of the various radii have been discussed previously in connection with Figure 6.

The traverse roll may be driven so that its R. P. M. is less than that of the package. The traverse roll radius is the radius to the outer surface of the roll. The traverse or cam groove tends to reduce the traverse radius as far as yarn location is concerned. However, the lateral travel of the yarn more than offsets any variation in groove depth.

While the package roll is supported on the end of a swinging arm, it is possible to provide cam slot or grooves in which the package axle may ride. In this way, the path of travel of the package axis, as the package size increases, need not necessarily be on the surface of a cylinder;

'What is claimed is:

1. In a yarn winding machine, the combination of spaced traverse and drive rolls, a bobbin support for carrying a bobbin upon which a package is to be wound by friction drive between the drive roll and package surface, means for mounting said bobbin support to move along a curved path whose axis is offset from but parallel to the axes of the drive and traverse rolls, a transverse section of the machine showing the drive roll center between the curved path center and traverse roll center, the three centers being in general alignment, the drive roll and traverse roll radii both being smaller than the maximum package radius, said maximum package radius being less than the curved path radius, said curved path, when extended, intersecting the line of centers between the traverse and drive rolls at a point nearer the drive roll then the transverse roll but outside the circumference of the drive roll, said bobbin center at the start of the package being upon one side of said intersection and moving away therefrom with increasing package size.

2. The machine according to claim 1 wherein the center of the drive roll is laterally offset from a line running between the center of the curved path and the center of the traverse roll, said package center and drive roll center at all times being on opposite sides of saidline, and wherein the broken line formed at the center of the drive roll between the lines of centers going to the center of the curved path and center of the traverse roll respectively forms an angle of between about 165 and about 180.

3. In a yarn winding machine, the combination of spaced traverse and drive rolls, a bobbin support for carrying a bobbin upon which a package is to be wound by friction drive between the drive roll and package surface, means for mounting said bobbin support to move along a curved path whose axis is offset from but parallel to the axes of the drive and traverse rolls, a transverse section of the machine showing the drive roll center offset somewhat from a line extending between the center of the curved path and center of traverse roll, the traverse roll radius being greater than the drive roll radius and being smaller than the radius arm of the curved path, the minimum and maximum package radii being respectively smaller and larger than the drive roll radius, the curved path, when extended, intersecting the line of centers between the traverse and drive rolls at a point nearer the drive roll than the traverse roll but outside the circumference of the drive roll, vsaid point of intersection and drive roll center being on one side of the line extendingbetween the center of the traverse roll and center of the curved path, the center of the package being at all times on the other side of said line, said various radii being so proportioned that the clearance between the package and traverse rolls remains generally constant over the range of variation of package radius, the clearance between traverse and drive rolls being smaller than the drive roll radius.

4. .In a 'yarn winding machine, thelcombination of spaced. traverseand drive rolls, a bobbin support for carrying a bobbin upon which a package is to be wound by friction drive between the drive roll and package surface,' aradius arm for supporting said bobbin support, meansfor mounting said radius arm so that it may have a limited range of movement around the end of said arm so that the bobbin support can move along a curved path whose axis is offset from but parallel to the axes of the drive and traverse rolls, a transverse section of the machine showing the drive roll center offset somewhat from a line extending between the center of the curved path and center of traverse roll, the traverse roll radius being greater than.the drive roll radius and smaller than the length of the radius arm, the minimum and maximum package radii being respectively smaller and larger than the drive roll radius, the curved path of the package roll center, when extended, intersecting the line of centers between the traverse and drive rolls at a point nearer the drive roll than the traverse roll but outside the circumference of the drive roll, said point of intersection and drive roll center being on one side of the line extending between the center of the traverse roll and center of the radius arm,,the center of the package being at all times on the other side of said line, a curved guide member, means for supporting said curved guide member so that its center is coincident with the center of travel of the package roll center, a block carried by said radius arm, a spring pressed finger carried by said block and riding on said guide, said guide having a recess at a point where said finger may lock when the package roll has been swung away from the drive roll and friction means carried by said machine for cooperation with said curved guide for steadying the movement of said radius arm as the package increases in radius.

5. In a yarn winding machine, the combination of spaced traverse and drive rolls, a bobbin support for carrying a bobbin upon which a package is to be wound by friction drive between the drive roll and package surface, means for mounting said bobbin support to move along a curved path whose axis is offset such a large distance as to render said curved path only slightly curved from a straight line, a transverse section of the machine showing the drive roll center between the curved path center and traverse roll center, the three centers being approximately in a straight line, the drive roll and traverse roll radii both being smaller than the maximum package radius, said maximum package radius being less than the curved path radius, said curved path, when extended, intersecting the line of centers between the traverse and drive rolls at a point nearer the drive roll than the traverse roll but outside the circurnference of the drive roll, said bobbin center at the start of the package being upon one side of said intersection and moving away therefrom with increasing package size.

6. A claim as set forth in claim 5 in which the radius of the curved path traveled by the bobbin support is great enough to always maintain the surface of the package within one and one-half inches of the surface of the traverse roll.

7. A claim as set forth in claim 6 in which the package surface is always between one-thirty-second and three-quarters of an inch away from the surface of the traverse roll.

References Cited in the file of this patent UNITED STATES PATENTS 1,749,355 Reece Mar. 4, 1930 2,226,152 Babcock Dec. 24, 1940 2,591,052 Camras Apr. 1, 1952 FOREIGN PATENTS 584,308 France Nov. 17, 1924 445,055 Great Britain, Apr. 2, 1936 

